EP1844285A2 - Echangeur thermique a tubes plats multicanaux - Google Patents

Echangeur thermique a tubes plats multicanaux

Info

Publication number
EP1844285A2
EP1844285A2 EP05855713A EP05855713A EP1844285A2 EP 1844285 A2 EP1844285 A2 EP 1844285A2 EP 05855713 A EP05855713 A EP 05855713A EP 05855713 A EP05855713 A EP 05855713A EP 1844285 A2 EP1844285 A2 EP 1844285A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
leg
recited
tube
heat exchange
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP05855713A
Other languages
German (de)
English (en)
Other versions
EP1844285A4 (fr
Inventor
Mikhail B Gorbounov
Igor B. Vaisman
Parmesh Verma
Lisa P. Sylvia
Xiaoyuan Chang
Gary D. Winch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP1844285A2 publication Critical patent/EP1844285A2/fr
Publication of EP1844285A4 publication Critical patent/EP1844285A4/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/22—Refrigeration systems for supermarkets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • This invention relates generally to heat exchangers having a plurality of parallel tubes extending between a pair of headers, also sometimes referred to as a manifolds, and, more particularly, to providing fluid expansion within the an header of a heat exchanger for improving distribution of fluid flow through the parallel tubes of the heat exchanger, for example a heat exchanger in a refrigerant vapor compression system.
  • Air conditioners and heat pumps employing refrigerant vapor compression cycles are commonly used for cooling or cooling/heating air supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility.
  • Refrigerant vapor compression systems are also commonly used for cooling air or other secondary fluid to provide a refrigerated environment for food items and beverage products, for example, within display cases in supermarkets, convenience stores, groceries, cafeterias, restaurants and other food service establishments.
  • these refrigerant vapor compression systems include a compressor, a condenser, an expansion device, and an evaporator connected in refrigerant flow communication.
  • the aforementioned basic refrigerant system components are interconnected by refrigerant lines in a closed refrigerant circuit and arranged in accord with the vapor compression cycle employed.
  • An expansion device commonly an expansion valve or a fixed-bore metering device, such as an orifice or a capillary tube, is disposed in the refrigerant line at a location in the refrigerant circuit upstream, with respect to refrigerant flow of the evaporator, and downstream of the condenser.
  • the expansion device operates to expand the liquid refrigerant passing through the refrigerant line running from the condenser to the evaporator to a lower pressure and temperature. In doing so, a portion of the liquid refrigerant traversing the expansion device expands to vapor.
  • the refrigerant flow entering the evaporator constitutes a two-phase mixture.
  • the particular percentages of liquid refrigerant and vapor refrigerant depend upon the particular expansion device employed and the refrigerant in use, for example Rl 2, R22, Rl 34a, R404A, R410A, R407C, R717, R744 or other compressible fluid.
  • the evaporator is a parallel tube heat exchanger.
  • Such heat exchangers have a plurality of parallel refrigerant flow paths therethrough provided by a plurality of tubes extending in parallel relationship between an inlet header and an outlet header.
  • the inlet header receives the refrigerant flow from the refrigerant circuit and distributes that refrigerant flow amongst the plurality of flow paths through the heat exchanger.
  • the outlet header serves to collect the refrigerant flow as it leaves the respective flow paths and to direct the collected flow back to the refrigerant line for return to the compressor in a single pass heat exchanger or through an additional bank of heat exchange tubes in a multi-pass heat exchanger.
  • parallel tube heat exchangers used in such refrigerant compression systems have used round tubes, typically having a diameter of 1/2 inch, 3/8 inch or 7millimeters.
  • multichannel tubes are being used in heat exchangers for refrigerant vapor compression systems.
  • Each mutli-channel tube has a plurality of flow channels extending longitudinally in parallel relationship the length of the tube, each channel providing a small cross-sectional flow area refrigerant flow path.
  • a heat exchanger with multi-channel tubes extending in parallel relationship between the inlet and outlet headers of the heat exchanger will have a relatively large number of small cross- sectional flow area refrigerant paths extending between the two headers.
  • a parallel tube heat exchanger with conventional round tubes will have a relatively small number of large flow area flow paths extending between the inlet and outlet headers.
  • Non-uniform distribution, also referred to as maldistibution, of two- phase refrigerant flow is a common problem in parallel tube heat exchangers which adversely impacts heat exchanger efficiency.
  • Two-phase maldistribution problems are caused by the difference in density of the vapor phase refrigerant and the liquid phase refrigerant present in the inlet header due to the expansion of the refrigerant as it traversed the upstream expansion device.
  • Obtaining uniform refrigerant flow distribution amongst the relatively large number of small cross-sectional flow area refrigerant paths is even more difficult than it is in conventional round tube heat exchangers and can significantly reduce heat exchanger efficiency.
  • a heat exchanger having a plurality of J-shaped, multi-channel, heat exchange tubes are connected in fluid communication between an inlet header defining a chamber for receiving a fluid to be distributed amongst the channels of the heat exchange tubes and an outlet header defining a chamber for collecting fluid having traversed the channels of the heat exchange tubes.
  • Each heat exchange tube has a plurality of fluid flow paths therethrough from an inlet end to an outlet end of the tube. The inlet end of each tube connects in fluid flow communication with the chamber of the inlet header and the outlet end of each tube connects in fluid flow communication with the chamber of the outlet header.
  • the fluid collecting in the chamber of the inlet header flows downwardly through the respective channels of a first leg of the J-shaped heat exchange tubes and thence upwardly through the respective channels of a second leg of the J-shaped tube.
  • the heat exchanger has an outlet header disposed above the inlet header.
  • a refrigerant vapor compression system in another aspect of the invention, includes a compressor, a condenser and an evaporative heat exchanger connected in refrigerant flow communication.
  • the evaporative heat exchanger includes a plurality of J-shaped, multi-channel, heat exchange tubes are connected in fluid communication between an inlet header defining a chamber for receiving a fluid to be distributed amongst the channels of the heat exchange tubes and an outlet header defining a chamber for collecting fluid having traversed the channels of the heat exchange tubes.
  • Each heat exchange tube has a plurality of fluid flow paths therethrough from an inlet end to an outlet end of the tube.
  • each tube connects in fluid flow communication with the chamber of the inlet header and the outlet end of each tube connects in fluid flow communication with the chamber of the outlet header.
  • the fluid collecting in the chamber of the inlet header flows downwardly through the respective channels of a first leg of the J-shaped heat exchange tubes and thence upwardly through the respective channels of a second leg of the J-shaped tube.
  • the heat exchanger has an outlet header disposed above the inlet header.
  • FIG. 1 is an elevation view of an embodiment of a heat exchanger in accordance with the invention
  • FIG. 2 is a side elevation view, partly sectioned, of the heat exchanger of Fig. 1;
  • FIG. 3 is a side elevation view, partly sectioned, of another exemplary embodiment of the heat exchanger depicted in Fig. 1;
  • FIG. 4 is a schematic illustration of a refrigerant vapor compression system incorporating the heat exchanger of the invention.
  • the heat exchanger 10 includes an inlet header 20, an outlet header
  • the inlet header 20 and the outlet header 30 comprise longitudinally elongated, hollow, closed end cylinders defining there within a fluid chamber having a circular cross-section.
  • the headers might comprise a longitudinally elongated, hollow, closed end cylinder having an elliptical cross-section or a longitudinally elongated, hollow, closed end body having a square, rectangular, hexagonal, octagonal, or other polygonal cross-section.
  • Each heat exchange tube 40 has a plurality of parallel flow channels
  • Each multi-channel heat exchange tube 40 is a "flat" tube of, for example, a rectangular or oval cross-section, defining an interior which is subdivided to form a side-by-side array of independent flow channels 42.
  • the flat, multi-channel tubes 40 may, for example, have a width of fifty millimeters or less, typically twelve to twenty-five millimeters, and a height of about two millimeters or less, as compared to conventional prior art round tubes having a diameter of either 1/2 inch, 3/8 inch or 7 mm.
  • Each heat exchanger tube 40 has its inlet end 43 opening through the wall of the inlet header 20 into fluid flow communication with the fluid chamber of the inlet header and has its outlet end 47 opening through the wall of the outlet header 30 into fluid flow communication with the fluid chamber of the outlet header 30.
  • each of the flow channels 42 of the respective heat exchange tubes 40 provides a flow path from the fluid chamber of the inlet header 20 to the fluid chamber of the outlet header 30.
  • the respective inlet ends 43 and outlet ends 47 of the heat exchange tubes 40 may be brazed, welded, adhesively bonded or otherwise secured in a corresponding mating slot in the wall of the header 20.
  • each multi-channel tube 40 will typically have about ten to twenty flow channels 42, but may have a greater or a lesser multiplicity of channels, as desired.
  • each flow channel 42 will have a hydraulic diameter, defined as four times the flow area divided by the perimeter, in the range from about 200 microns to about 3 millimeters.
  • the channels 42 may have rectangular, triangular, trapezoidal cross-section or any other desired non- circular cross-section.
  • the heat exchange tubes 40 are generally J-shaped having a base bend 44, a first leg 46 extending generally vertically upwardly from one end of the base bend 44, and a second leg 48 extending generally vertically upwardly from the other end of the base bend 44.
  • Both the inlet header 20 and the outlet header 30 are disposed at a higher elevation than the base bend 44. Further, the outlet header 30 is disposed at a higher elevation than the inlet header 20.
  • the inlet ends 43 of the first legs 46 of the respective heat exchange tubes 40 enter the inlet header 20 through the bottom of the header.
  • the fluid collecting in the chamber of the inlet header flows downwardly through the respective channels 42 of the first leg 46 of the J-shaped heat exchange tubes 40 and thence upwardly through the respective channels 42 of the second leg 48 of the J-shaped heat exchange tubes 40 and into the fluid chamber of the outlet header 30.
  • each generally J-shape heat exchange tube 40 has a base bend 44 that extends horizontally between the vertically extending relatively shorter leg 46, which is in fluid flow communication with the fluid chamber of the inlet header 20, and the vertically extending relatively longer leg 48, which is in fluid flow communication with the fluid chamber of the outlet header 30.
  • each generally J-shaped heat exchange tube 40 has a base bend 44 that constitutes a relatively sharp, somewhat v-shape bend.
  • the generally J-shape heat exchange 40 somewhat resembles a checkmark with the base bend 44 disposed between the generally upwardly, but not vertically, extending relatively shorter leg 46, which is in fluid flow communication with the fluid chamber of the inlet header 20, and the generally upwardly, but not vertically, extending relatively longer leg 48, which is in fluid flow communication with the fluid chamber of the outlet header 30.
  • a refrigerant compression system 100 is depicted schematically having a compressor 60, a condenser 70, an expansion valve 50, and the heat exchanger 10 of the invention functioning as an evaporator, connected in a closed loop refrigerant circuit by refrigerant lines 12, 14 and 16.
  • the compressor 60 circulates hot, high pressure refrigerant vapor through refrigerant line 12 into the inlet header of the condenser 70, and thence through the heat exchanger tubes of the condenser wherein the hot refrigerant vapor condenses to a liquid as it passes in heat exchange relationship with a cooling fluid, such as ambient air which is passed over the heat exchange tubes by the condenser fan 72.
  • a cooling fluid such as ambient air which is passed over the heat exchange tubes by the condenser fan 72.
  • the high pressure, liquid refrigerant collects in the outlet header of the condenser 70 and thence passes through refrigerant line 14 to the inlet header 20 of the evaporator 10.
  • the refrigerant thence passes through the generally J-shape heat exchanger tubes 40 of the evaporator 10 wherein the refrigerant is heated as it passes in heat exchange relationship with air to be cooled which is passed over the heat exchange tubes 40 by the evaporator fan 80.
  • the refrigerant vapor collects in the outlet header 30 of the evaporator 10 and passes therefrom through refrigerant line 16 to return to the compressor 60 through the suction inlet thereto.
  • the heat exchanger of the invention may be employed in refrigerant compression systems of various designs, including, without limitation, heat pump cycles, economized cycles and commercial refrigeration cycles.
  • expansion valve 50 As the high pressure condensed refrigerant liquid passes through refrigerant line 14 from the outlet header of the condenser to the inlet header of the evaporator, it traverses then expansion valve 50. In the expansion valve 50, the high pressure, liquid refrigerant is partially expanded either to lower pressure, liquid refrigerant or, more commonly, to a low pressure liquid/vapor refrigerant mixture.
  • two-phase maldistribution problems are caused by the difference in density of the vapor phase refrigerant and the liquid phase refrigerant when a two-phase mixture is present in the inlet header 20 due to the expansion of the refrigerant as it traversed the upstream expansion device.
  • the vapor phase refrigerant being less dense than the liquid phase refrigerant, will naturally tend to separate and migrate upwardly within the header and collect above the level of the liquid phase refrigerant within the fluid chamber of the inlet header. Because the heat exchange tubes 40 open into the fluid chamber of the inlet header 20 through the bottom therefore, the openings to the flow channels 42 of the heat exchange tubes 40 will open into the fluid chamber beneath the surface of the liquid phase refrigerant.
  • gravity will assist in distributing the liquid refrigerant collected within the inlet header 20 amongst the multiplicity of channels 42 of the plurality of heat exchange tubes 40 opening to the fluid chamber of the inlet header 20. Further, gravity assists in impeding the channeling of vapor phase refrigerant preferentially through some channels 42, while other channels receive limited vapor phase refrigerant, and results in the vapor phase refrigerant being more uniformly distributed, generally by entrainment, throughout the liquid phase refrigerant.
  • the distribution of and the quality of the refrigerant entering the plurality of tubes multi-channel tubes 40 will be more uniform in the heat exchanger of the invention having generally J-shape heat exchange tubes as compared to conventional straight tube heat exchangers wherein the refrigerant passes upwardly from the inlet header into the flow passages defined by the those tubes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un échangeur thermique qui comprend une pluralité de tubes d'échange thermique multicanaux aplatis en forme générale de J s'étendant entre un collecteur d'admission et un collecteur d'évacuation. Chaque tube d'échange thermique comprend un coude de base qui s'étend horizontalement entre le montant relativement court qui s'étend verticalement et qui est en communication fluidique avec la chambre de fluide du collecteur d'admission, et le montant relativement long qui s'étend verticalement et qui est en communication fluidique avec la chambre de fluide du collecteur d'évacuation.
EP05855713A 2005-02-02 2005-12-28 Echangeur thermique a tubes plats multicanaux Withdrawn EP1844285A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US64943305P 2005-02-02 2005-02-02
PCT/US2005/047199 WO2006083435A2 (fr) 2005-02-02 2005-12-28 Echangeur thermique a tubes plats multicanaux

Publications (2)

Publication Number Publication Date
EP1844285A2 true EP1844285A2 (fr) 2007-10-17
EP1844285A4 EP1844285A4 (fr) 2011-12-21

Family

ID=36777698

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05855713A Withdrawn EP1844285A4 (fr) 2005-02-02 2005-12-28 Echangeur thermique a tubes plats multicanaux

Country Status (10)

Country Link
US (1) US8091620B2 (fr)
EP (1) EP1844285A4 (fr)
JP (1) JP2008528936A (fr)
KR (1) KR20070091200A (fr)
CN (1) CN100592017C (fr)
AU (1) AU2005326703A1 (fr)
BR (1) BRPI0519937A2 (fr)
CA (1) CA2595844A1 (fr)
MX (1) MX2007009255A (fr)
WO (1) WO2006083435A2 (fr)

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10333577A1 (de) * 2003-07-24 2005-02-24 Bayer Technology Services Gmbh Verfahren und Vorrichtung zur Entfernung von flüchtigen Substanzen aus hochviskosen Medien
WO2008064219A1 (fr) 2006-11-22 2008-05-29 Johnson Controls Technology Company Évaporateur multicanaux avec collecteur de mélange de flux
KR101518205B1 (ko) 2006-11-22 2015-05-08 존슨 컨트롤스 테크놀러지 컴퍼니 다른 멀티채널 튜브를 갖는 멀티채널 열 교환기
US8166776B2 (en) 2007-07-27 2012-05-01 Johnson Controls Technology Company Multichannel heat exchanger
US20090025405A1 (en) 2007-07-27 2009-01-29 Johnson Controls Technology Company Economized Vapor Compression Circuit
EP2037199A1 (fr) * 2007-09-13 2009-03-18 Behr France Rouffach SAS Caloporteur
KR200447300Y1 (ko) 2008-04-23 2010-01-13 한국남동발전 주식회사 수직 펌프 모터의 베어링 오일 쿨러
WO2009151434A1 (fr) * 2008-06-09 2009-12-17 Otis Elevator Company Moteur et transmission de machinerie d'ascenseur, et leur refroidissement
WO2010005918A2 (fr) * 2008-07-09 2010-01-14 Carrier Corporation Pompe à chaleur avec échangeurs thermiques à micro-canaux en tant qu’échangeur thermique extérieur et échangeur réchauffeur
CN102099651B (zh) * 2008-07-15 2013-12-25 开利公司 集成多回路微通道换热器
US8234881B2 (en) 2008-08-28 2012-08-07 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US8596089B2 (en) * 2009-02-26 2013-12-03 Honeywell International Inc. Refrigerant distribution system
TWI490194B (zh) * 2009-09-18 2015-07-01 Eternal Chemical Co Ltd 可聚合組合物及其用途
US8439104B2 (en) 2009-10-16 2013-05-14 Johnson Controls Technology Company Multichannel heat exchanger with improved flow distribution
CN101846465B (zh) * 2010-04-13 2011-11-09 三花丹佛斯（杭州）微通道换热器有限公司 换热器
DE102010061768A1 (de) * 2010-11-23 2012-05-24 Behr Gmbh & Co. Kg Vorrichtung zur Kühlung einer Wärmequelle eines Kraftfahrzeugs
EP2584301B1 (fr) 2011-10-19 2014-08-13 WS-Wärmeprozesstechnik GmbH Caloporteur à température élevée
WO2014186440A2 (fr) 2013-05-14 2014-11-20 President And Fellows Of Harvard College Production rapide de gouttelettes
WO2015025365A1 (fr) * 2013-08-20 2015-02-26 三菱電機株式会社 Échangeur de chaleur, climatiseur et dispositif à cycle frigorifique
WO2016036732A1 (fr) * 2014-09-05 2016-03-10 Carrier Corporation Échangeur de chaleur à microcanaux tolérant au gel pour pompe à chaleur et applications de réfrigération
EP3224565B1 (fr) * 2014-11-26 2023-12-27 Carrier Corporation Échangeur de chaleur à microcanaux tolérant au gel
CN107429977B (zh) 2015-02-18 2019-08-16 达纳加拿大公司 具有顶部歧管和底部歧管的堆叠板热交换器
US11193715B2 (en) * 2015-10-23 2021-12-07 Hyfra Industriekuhlanlagen Gmbh Method and system for cooling a fluid with a microchannel evaporator
CN106642826B (zh) * 2015-10-28 2019-04-19 丹佛斯微通道换热器（嘉兴）有限公司 换热器
CN106679209A (zh) * 2015-11-10 2017-05-17 丹佛斯微通道换热器（嘉兴）有限公司 制冷系统
ES2930282T3 (es) * 2016-05-03 2022-12-09 Carrier Corp Disposición de intercambiadores de calor
CN107806777B (zh) 2016-09-09 2020-12-04 丹佛斯微通道换热器（嘉兴）有限公司 无翅片换热器
CN108050696B (zh) * 2017-10-24 2020-03-06 山东科技大学 一种微通道丙烷直膨式太阳能热泵热水器
EP3737902A4 (fr) * 2018-01-12 2021-10-20 Schneider Electric IT Corporation Système de réglage de la pression d'un collecteur
US20190368819A1 (en) * 2018-05-30 2019-12-05 Johnson Controls Technology Company Heat exchanger for hvac unit
JP6912673B2 (ja) * 2019-07-22 2021-08-04 株式会社前川製作所 デフロストシステム
US11493277B2 (en) * 2019-11-06 2022-11-08 Carrier Corporation Microchannel heat exchanger
CN115388674B (zh) * 2021-05-25 2025-03-11 丹佛斯有限公司 换热器和具有该换热器的空调系统
CN219347480U (zh) * 2023-01-17 2023-07-14 浙江盾安热工科技有限公司 换热器扁管、换热器扁管组件及换热器
CN118274651B (zh) * 2024-06-03 2024-07-30 合肥工业大学 适用于混合动力汽车的多介质集成换热器及其控制方法

Family Cites Families (55)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1843132A (en) * 1928-05-12 1932-02-02 Superheater Co Ltd Superheater
US1884555A (en) * 1930-07-15 1932-10-25 Griscom Russell Co Scale shedding heat transfer apparatus
US2297633A (en) * 1940-02-26 1942-09-29 Nash Kelvinator Corp Refrigerating apparatus
US2502675A (en) * 1946-12-23 1950-04-04 Modine Mfg Co Cleanable type heat exchanger
US2591109A (en) * 1948-07-15 1952-04-01 Bohn Aluminium & Brass Corp Refrigerant evaporator
US2612350A (en) * 1948-09-17 1952-09-30 Griscom Russell Co Expansion compensated countercurrent heat exchanger
FR1258044A (fr) 1960-05-25 1961-04-07 Lummus Nederland N V échangeur de chaleur
US3231013A (en) * 1961-01-27 1966-01-25 Licencia Talalmanyokat Controlling the heat exchangers of air condensation apparatus
DE2256633C3 (de) * 1972-11-17 1975-10-30 Siemens Ag, 1000 Berlin Und 8000 Muenchen Dampferzeuger
DE2300920C3 (de) * 1973-01-09 1982-12-09 Siemens AG, 1000 Berlin und 8000 München Bedienungspult für eine Röntgendiagnostikeinrichtung
US3920069A (en) 1974-03-28 1975-11-18 Modine Mfg Co Heat exchanger
US4088182A (en) * 1974-05-29 1978-05-09 The United States Of America As Represented By The United States Department Of Energy Temperature control system for a J-module heat exchanger
US4382468A (en) 1979-05-17 1983-05-10 Hastwell P J Flat plate heat exchanger modules
JPS56108097A (en) * 1980-01-30 1981-08-27 Toyo Eng Corp Heat exchanger
US4497363A (en) * 1982-04-28 1985-02-05 Heronemus William E Plate-pin panel heat exchanger and panel components therefor
JPS59122803A (ja) 1982-12-27 1984-07-16 株式会社東芝 蒸気タ−ビンの再熱装置
US4724904A (en) 1984-11-23 1988-02-16 Westinghouse Electric Corp. Nuclear steam generator tube orifice for primary temperature reduction
US5279360A (en) * 1985-10-02 1994-01-18 Modine Manufacturing Co. Evaporator or evaporator/condenser
US4998580A (en) 1985-10-02 1991-03-12 Modine Manufacturing Company Condenser with small hydraulic diameter flow path
FR2591729A1 (fr) 1985-12-13 1987-06-19 Chausson Usines Sa Echangeur du type evaporateur a faisceau tubulaire
JPH064217Y2 (ja) * 1987-05-28 1994-02-02 信和産業株式会社 熱交換器
JPH02217764A (ja) 1989-02-17 1990-08-30 Matsushita Electric Ind Co Ltd 膨張弁
JPH0480575A (ja) 1990-07-20 1992-03-13 Technol Res Assoc Super Heat Pump Energ Accum Syst 冷媒分配器
US5314013A (en) * 1991-03-15 1994-05-24 Sanden Corporation Heat exchanger
JPH0674677A (ja) 1992-08-27 1994-03-18 Mitsubishi Heavy Ind Ltd 積層型熱交換器の製造方法
EP0586037B1 (fr) 1992-09-03 1997-05-21 Modine Manufacturing Company Echangeur de chaleur
JP3330176B2 (ja) 1993-02-19 2002-09-30 株式会社日立製作所 ヒートポンプ用パラレルフロー熱交換器
US5415223A (en) 1993-08-02 1995-05-16 Calsonic International, Inc. Evaporator with an interchangeable baffling system
JP3305460B2 (ja) * 1993-11-24 2002-07-22 昭和電工株式会社 熱交換器
JPH07301472A (ja) 1994-05-09 1995-11-14 Matsushita Refrig Co Ltd ヘッダー
DE4439801C2 (de) 1994-11-08 1996-10-31 Gea Power Cooling Systems Inc Luftbeaufschlagter Trockenkühler
DE4442040A1 (de) 1994-11-25 1996-05-30 Behr Gmbh & Co Wärmetauscher mit einem Sammelrohr
IT1276990B1 (it) 1995-10-24 1997-11-03 Tetra Laval Holdings & Finance Scambiatore di calore a piastre
JP3007839B2 (ja) 1996-03-13 2000-02-07 松下冷機株式会社 分流器
JPH10185463A (ja) 1996-12-19 1998-07-14 Sanden Corp 熱交換器
US5826649A (en) 1997-01-24 1998-10-27 Modine Manufacturing Co. Evaporator, condenser for a heat pump
HU9700240D0 (en) * 1997-01-27 1997-03-28 Energiagazdalkodasi Intezet Air-cooled steam condenser
DE19719252C2 (de) * 1997-05-07 2002-10-31 Valeo Klimatech Gmbh & Co Kg Zweiflutiger und in Luftrichtung einreihiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage
JPH1144498A (ja) * 1997-05-30 1999-02-16 Showa Alum Corp 熱交換器用偏平多孔チューブ及び同チューブを用いた熱交換器
US5967228A (en) 1997-06-05 1999-10-19 American Standard Inc. Heat exchanger having microchannel tubing and spine fin heat transfer surface
JP4080575B2 (ja) 1997-08-14 2008-04-23 株式会社東芝 紙葉類処理装置
US5910167A (en) 1997-10-20 1999-06-08 Modine Manufacturing Co. Inlet for an evaporator
US5941303A (en) 1997-11-04 1999-08-24 Thermal Components Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same
FR2793014B1 (fr) 1999-04-28 2001-07-27 Valeo Thermique Moteur Sa Echangeur de chaleur pour fluide sous pression elevee
JP4026277B2 (ja) 1999-05-25 2007-12-26 株式会社デンソー 熱交換器
JP2000346568A (ja) 1999-05-31 2000-12-15 Mitsubishi Heavy Ind Ltd 熱交換器
JP2001165532A (ja) * 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
US6439300B1 (en) 1999-12-21 2002-08-27 Delphi Technologies, Inc. Evaporator with enhanced condensate drainage
JP2002022313A (ja) 2000-07-06 2002-01-23 Matsushita Refrig Co Ltd 分流器
EP1370818A4 (fr) 2001-02-19 2006-04-26 Showa Denko Kk Echangeur thermique
KR100906769B1 (ko) * 2002-01-31 2009-07-10 한라공조주식회사 오뚜기형 유로를 갖는 열교환기용 튜브 및 이를 이용한열교환기
JP4107051B2 (ja) 2002-02-19 2008-06-25 株式会社デンソー 熱交換器
US6688138B2 (en) * 2002-04-16 2004-02-10 Tecumseh Products Company Heat exchanger having header
US6688137B1 (en) 2002-10-23 2004-02-10 Carrier Corporation Plate heat exchanger with a two-phase flow distributor
CN1566870A (zh) 2003-06-17 2005-01-19 乐金电子(天津)电器有限公司 热交换器的连接装置

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US20080041092A1 (en) 2008-02-21
KR20070091200A (ko) 2007-09-07
WO2006083435A3 (fr) 2007-08-23
HK1117898A1 (zh) 2009-01-23
BRPI0519937A2 (pt) 2009-09-08
AU2005326703A1 (en) 2006-08-10
US8091620B2 (en) 2012-01-10
CA2595844A1 (fr) 2006-08-10
JP2008528936A (ja) 2008-07-31
MX2007009255A (es) 2007-09-04
EP1844285A4 (fr) 2011-12-21
CN100592017C (zh) 2010-02-24
CN101120222A (zh) 2008-02-06

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